US8827659B2 - Oil supply apparatus - Google Patents
Oil supply apparatus Download PDFInfo
- Publication number
- US8827659B2 US8827659B2 US13/878,626 US201113878626A US8827659B2 US 8827659 B2 US8827659 B2 US 8827659B2 US 201113878626 A US201113878626 A US 201113878626A US 8827659 B2 US8827659 B2 US 8827659B2
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- US
- United States
- Prior art keywords
- oil
- oil passage
- discharge port
- work
- land
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C14/12—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
Definitions
- the present invention relates to an oil supply apparatus for use in e.g. lubrication of an automobile engine and controlling of a hydraulically controlled device.
- work oil is employed for e.g. lubrication of an automobile engine, controlling of a hydraulically controlled device (a hydraulic control valve etc.).
- a hydraulically controlled device a hydraulic control valve etc.
- Such work oil is fed to respective parts of the automobile by an oil supply apparatus, and this oil supply apparatus includes a discharge amount varying arrangement capable of appropriately adjusting the discharge pressure of work oil in accordance with a rotational speed of the engine.
- Patent Document 1 An example of this type of oil supply apparatus is known from Patent Document 1 identified below.
- the oil supply apparatus disclosed in Patent Document 1 includes a pump body having a suction port for suctioning work oil in association with rotation of a rotor which is driven in synchronism with a crank shaft as well as a first discharge port and a second discharge port that discharge work oil in association with the rotation of the rotor.
- this oil supply apparatus further includes a first oil passage for feeding at least work oil from the first discharge port to a work oil fed section, a second oil passage for feeding work oil from the second discharge port to the first oil passage, and a relief oil passage for feeding work oil from a hydraulic control valve including a valve body operable in response to oil pressure of the work oil to the first oil passage to at least one of the suction port and an oil pan.
- the valve body is provided with a first valve body oil passage and a second valve body oil passage. And, when the oil pressure of the work oil to the first oil passage is within a predetermined range, the work oil from the second discharge port is fed via the first valve body oil passage to the first oil passage; whereas when the oil pressure of the work oil to the first oil passage is above the predetermined range, the work oil from the second discharge port is fed via the second valve body oil passage to the first oil passage.
- the feed amount of work oil to the first oil passage in this situation is the sum of the discharge amount of the first discharge port and the discharge amount of the second discharge port.
- the above-described arrangement is made such that when the oil pressure of the work oil to the first oil passage is above the predetermined range, the work oil from the second discharge port is fed via the second valve body oil passage to the first oil passage.
- the feeding amount of work oil to the first oil passage can again comprise the sum of the discharge amount of the first discharge port and the discharge amount of the second discharge port.
- Patent Document 1 Japanese Unexamined Patent Application Publication No. 2005-140022
- the object of the present invention is to provide a compact oil supply apparatus.
- an oil supply apparatus comprises:
- a pump body including a suction port for suctioning work oil in association with rotation of a rotor driven by a drive source, and a first discharge port and a second discharge port that discharge work oil in association with the rotation of the rotor;
- a first oil passage for feeding at least work oil from the first discharge port to the feed oil passage
- a second oil passage for feeding work oil from the second discharge port to a valve chamber
- a return oil passage for returning work oil from the valve chamber to at least one of the suction port and an oil pan
- a hydraulic control valve having a valve body operable in response to the oil pressure of work oil fed to the feed oil passage for connecting/disconnecting the second oil passage to/from the first oil passage and the return oil passage;
- valve body includes a first land and a second land that protrude along the radial direction of the valve body about the axis of the valve body, and a small diameter portion connecting the first land and the second land along the axial direction, the small diameter portion having a smaller diameter than at least the outer diameter of the first land and the second land;
- rotational speeds of the rotor are set as a first rotational range, a second rotational range and a third rotational range in the ascending order;
- the outer diameter of the first land is larger than the outer diameter of the second land.
- a gap can be provided between an inner wall portion of the valve chamber in which the first land is slidable and the second land. Therefore, it becomes possible to utilize this gap as a communication passage through which the work oil is caused to flow.
- a return port communicated to the return oil passage is valve-closed by the first land.
- a return port communicated to the return oil passage is valve-opened, and the first oil passage and the second oil passage are partitioned from each other.
- a return port communicated to the return oil passage is valve-opened, and the first oil passage and the second oil passage are communicated to each other.
- FIG. 1 is a view schematically showing an oil supply apparatus
- FIG. 2 is a view showing an example in which the oil supply apparatus is applied to an engine of an automobile
- FIG. 3 is a view schematically showing flow of work oil in case a rotor rotational speed is in a low speed range
- FIG. 4 is a view schematically showing flow of work oil in case a rotor rotational speed is in a first intermediate range
- FIG. 5 is a view schematically showing flow of work oil in case a rotor rotational speed is in a first intermediate range
- FIG. 6 is a view schematically showing flow of work oil in case a rotor rotational speed is in a second intermediate range
- FIG. 7 is a view schematically showing flow of work oil in case a rotor rotational speed is in a high speed range
- FIG. 8 is a graph showing relationship between rotor rotational speeds and discharge amounts of work oil.
- An oil supply apparatus 100 relating to the present invention has a function of feeding efficiently an amount of work oil to a work oil fed device (“a work oil fed section 7 ”) in association with rotation of a rotor 2 which is driven in synchronism with a drive source such as a crank shaft of an automobile.
- FIG. 1 schematically shows the oil supply device 100 .
- FIG. 2 shows the oil supply device 100 as being mounted in an engine of an automobile.
- the oil supply apparatus 100 includes a pump body 1 , a hydraulic control valve 4 , an oil feed passage 5 , a first oil passage 61 , a second oil passage 62 and a return oil passage 66 .
- the pump body 1 is formed of metal (e.g. an aluminum alloy, an iron alloy, etc.) and a pump chamber 10 is formed inside this pump body 1 .
- the pump chamber 10 forms an inner gear portion 12 constituting a driven gear having many inner teeth 11 .
- a rotor 2 formed of metal.
- the rotor 2 is connected to a crank shaft 70 of the automobile engine as a drive source and is rotated in unison with the crank shaft 70 .
- the rotational speed of the rotor 2 is designed to range e.g. from 600 to 7000 rpm approximately.
- the rotor 2 forms an outer gear portion 22 constituting a drive gear having many outer teeth 21 .
- the inner teeth 11 and the outer teeth 21 are defined by a mathematical curve such as a trochoid curve, a cycloid curve, etc.
- the rotational direction of the rotor 2 is a direction denoted with an arrow A 1 .
- the outer teeth 21 of the rotor 2 come into engagement with the inner teeth 11 one after another, so that the inner gear portion 12 too is rotated in the same direction.
- the outer teeth 21 and the inner teeth 11 form therebetween gaps 22 a - 22 k .
- the gap 22 k has the largest volume and the gaps 22 e and 22 f have the smallest volume.
- the volume increases progressively, thereby to generate a suction pressure, whereby a suction effect for the work oil is obtained.
- the gaps 21 j - 22 f have progressively smaller volumes, there is generated a discharge pressure, so that a discharge effect for the work oil is obtained.
- the pump body 1 forms a discharge port group 33 including a first discharge port (a main discharge port) 31 and a second discharge port (an auxiliary discharge port) 32 . That is, the discharge port group 33 comprises ports for discharging work oil from the pump chamber 10 in association with rotation of the rotor 2 .
- the main discharge port 31 has end sides 31 a , 31 c and the auxiliary discharge portion 32 has end sides 32 a , 32 c .
- the pump body 1 forms a suction port 36 .
- the suction port 36 is a port for suctioning an amount of work oil into the pump chamber 10 in association with rotation of the rotor 2 .
- the suction port 36 has end sides 36 a , 36 c.
- the suction port 36 is located at the start point and the main discharge port 31 is located upstream of the auxiliary discharge port 32 .
- the aperture area of the main discharge port 31 is set larger than the aperture area of the auxiliary discharge port 32 .
- the area difference or area ratio between the aperture area of the main discharge port 31 and the aperture area of the auxiliary discharge port 32 is not particularly limited. Further, in case the aperture area of the main discharge port 31 and the aperture area of the auxiliary discharge port 32 are designed to be same as or different from each other, whichever one of the aperture area of the main discharge port 31 and the aperture area of the auxiliary discharge port 32 can be set larger than the other.
- the main discharge port 31 and the auxiliary discharge port 32 are partitioned from each other by a partitioning portion 37 , so that these ports have discharging functions independently of each other.
- a partitioning portion 37 the width along the circumferential direction of the rotor 2
- the feed oil passage 5 is an oil passage for feeding work oil to the work oil fed section 7 .
- the work oil fed section 7 can be e.g. a lubrication device needing oil feeding, such as a slide bearing, a bearing, etc., or a valve moving mechanism of an engine, a drive mechanism of the engine such as a cylinder, a piston, etc.
- the first oil passage 61 is an oil passage connecting between the main discharge port 31 and the feed oil passage 5 . Therefore, this passage has a function of feeding work oil discharged at least from the main discharge port 31 to the feed oil passage 5 .
- the second oil passage 62 is an oil passage for connecting a valve chamber 40 of the hydraulic control valve 4 to be described later and the auxiliary discharge port 32 . Therefore, this passage has a function of feeding work oil discharged from the auxiliary discharge port 32 to the valve chamber 40 . In this, the work oil discharged from the auxiliary discharge port 32 is fed via the valve chamber 40 and the first oil passage 61 to the feed oil passage 5 .
- the return oil passage 66 is an oil passage for returning work oil from the valve chamber 40 to at least one of the suction port 36 and an oil pan 69 .
- the return oil passage 66 is shown in the form of returning the oil to the suction port 36 .
- a passage 66 n for suctioning work oil form the oil pan 69 is provided to be communicated to the suction port 36 .
- the hydraulic control valve 4 includes a valve body 47 operable in response to the oil pressure of the work oil fed to the feed oil passage 5 and the valve chamber 40 slidably accommodating this valve body 47 .
- the valve body 47 is accommodated in the valve chamber 40 as being urged in a direction of an arrow B 1 by a spring 49 .
- the valve body 47 includes two radially protruding portions that protrude along the radial direction of the valve body 47 about the axis of this valve body 47 . These two radially protruding portions correspond to a first land 47 X and a second land 47 Y
- the first land 47 X and the second land 47 Y are provided respectively in the form of cylinders coaxial with the valve body 47 and provided at opposed axial ends of the valve body 47 .
- the outer diameter of the first land 47 X is set larger than the outer diameter of the second land 47 Y.
- the valve body 47 further includes a small-diameter portion 47 a smaller than the outer diameters of the first land 47 X and the second land 47 Y. Therefore, the first land 47 X, the small-diameter portion 47 a and the second land 47 Y together form an inter-land space 47 c.
- valve chamber 40 of the hydraulic control valve 4 includes a valve port 41 , a return port 42 and a drain port 43 .
- the valve port 41 is provided in a second inner wall portion 56 of the valve chamber 40 and communicated to the second oil passage 62 . With this, it becomes possible to introduce work oil from the second discharge port 32 into the valve chamber 40 .
- the return port 42 is provided in a first inner wall portion 55 of the valve chamber 40 and communicated to the return oil passage 66 . With this, it becomes possible to return the work oil from the hydraulic control valve 4 to the suction port 36 .
- the drain port 43 too is provided in the first inner wall portion 55 of the valve chamber 40 and communicated to the return oil passage 66 . With this, as work oil is suctioned or discharged via the drain port 43 to/from the valve chamber 40 , the valve body 47 can slide smoothly.
- the outer diameter of the first land 47 X is formed in correspondence with the inner diameter of the first inner wall portion 55 so that this first land 47 X may slide along the inner peripheral face of the first inner wall portion 55 along the axial direction of the valve body 47 .
- the outer diameter of the second land 47 Y is formed in correspondence with the inner diameter of the second inner wall portion 56 so that this second land 47 Y may slide along the inner peripheral face of the second inner wall portion 56 along the axial direction of the valve body 47 .
- the outer diameter of the first land 47 X is formed larger than the outer diameter of the second land 47 Y as described above.
- the inner diameter of the first inner wall portion 55 of the valve chamber 40 slidably accommodating the first land 47 X is formed greater than the inner diameter of the second inner wall portion 56 of the valve chamber 40 slidably accommodating the second land 47 Y.
- the above-described partitioning portion 37 constitutes a part of the second inner wall portion 56 .
- the outer diameter of the first land 47 X is formed e.g. about a few micro meters smaller than the inner diameter of the first inner wall portion 55 .
- the outer diameter of the second land 47 Y is formed e.g. about a few micro meters smaller than the inner diameter of the second inner wall portion 56 . Therefore, the first inner wall portion 55 , the second inner wall portion 56 , the first land 47 X and the second land 47 Y are set in the ascending order of the diameters thereof as the inner diameter of the first inner wall portion 55 , the outer diameter of the first land 47 X, the inner diameter of the second inner wall portion 56 and the outer diameter of the second land 47 Y.
- an inner diameter varying portion 57 is formed between the first inner wall portion 55 and the second inner wall portion 56 .
- This inner diameter varying portion 57 is provided to continuously connect the first inner wall portion 55 and the second inner wall portion 56 . Therefore, the valve body 47 accommodated in the valve chamber 40 while being urged by the spring 49 in the direction of arrow B 1 is restricted by the inner diameter varying portion 57 . With this, the valve body 47 establishes or break communication between the second oil passage 62 and either the first oil passage 61 or the return oil passage 66 .
- the language “establish or brake” means realization of communication or non-communication therebetween.
- valve body 47 causes the second oil passage 62 to be communicated to the first oil passage 61 and the return oil passage 66 or causes the passage 62 not to be communicated thereto. Modes of such communication establishment or break between the second oil passage 62 and the first oil passage 61 and the return oil passage 66 will be detailed later.
- the inventive oil supply apparatus 100 is configured as described above.
- the valve body 47 of the hydraulic control valve 4 provides supply modes A-E to be described next.
- the rotational speeds of the rotor 2 are set as a first rotational range, a second rotational range and a third rotational range in the ascending order.
- valve driving force F 1 is smaller than an urging force F 3 of the spring 49 (F 1 ⁇ F 3 ), then, the valve body 47 is moved in the arrow B 1 direction by the spring 49 ( FIG. 1 ). With this, the return port 42 communicated to the return oil passage 66 is valve-closed by the outer peripheral face of the first land 47 X.
- the first land 47 X of the valve body 47 valve-closes the return port 42 and also communication is established between the valve port 41 and the first oil passage 61 .
- the small-diameter portion 47 a and the partitioning portion 37 together form a first communication passage 91 . Accordingly, it becomes possible to feed the work oil from the auxiliary discharge port 32 via the small diameter portion 47 a , that is, via the first communication passage 91 , to the first oil passage 61 .
- the feeding amount of work oil to the feed oil passage 5 becomes the sum of the discharge mount of the main discharge port 31 and the discharge mount of the auxiliary discharge port 32 .
- the oil amount fed to the feed oil passage 5 exhibits a characteristics indicated by O-P line in FIG. 8 ; that is, in association with increase in the rotational speed of the rotor 2 , the discharge amount of work oil from the main discharge port 31 increases and the oil pressure of the first oil passage 61 increases; and also the discharge amount of work oil from the auxiliary discharge port 32 increases and the oil pressure of the second oil passage 62 increases.
- the rotational speed of the rotor 2 increases and this rotational speed of the rotor 2 exceeds a predetermined rotational speed (N 1 : e.g. 1500 rpm).
- N 1 e.g. 1500 rpm.
- This first intermediate speed range As the valve driving force Fl increases to overwhelm the urging force F 3 of the spring 49 (F 1 >F 3 ), the valve body 47 will be moved in the arrow B 2 direction (see FIG. 1 ) until the valve driving force F 1 becomes balanced with or equal to the urging force F 3 .
- This first intermediate speed range corresponds to the “second rotational range”.
- the return port 42 communicated to the return oil passage 66 is valve-opened. Also, the communication between the valve port 41 and the first oil passage 61 is maintained. That is, there is provided an intermediate condition in the course of shifting of the valve body 47 to a supply mode D to be described below. With this, a second communication passage 92 is formed by the small-diameter portion 47 a and the first inner wall portion 55 . Therefore, it becomes possible to feed the work oil from the auxiliary discharge port 32 via the small-diameter portion 47 a , that is, via the second communication passage 92 , to the return oil passage 66 . Further, a portion of the work oil from the main discharge port 31 too is fed via the first oil passage 91 to the return oil passage 66 .
- the feed amount of work oil to the feed oil passage 5 becomes a portion of the discharge amount of the main discharge port 31 .
- the oil amount fed to the feed oil passage 5 exhibits a characteristics indicated by P-Q line in FIG. 8 . That is, as communication is established between the auxiliary discharge port 32 and the return oil passage 66 , the ratio in the increase of the discharge amount in response to increase in the rotational speed of the rotor 2 becomes smaller.
- FIG. 8 shows the relationship between the required oil amounts of VVT (valve timing control apparatus) as the work oil fed section 7 and the rotor rotational speeds of the engine.
- VVT valve timing control apparatus
- the oil supply apparatus 100 is configured such that the respective slopes of the characteristics curves O-P and.
- the oil supply apparatus 100 may be alternatively configured that the slopes extend over the required oil amount of any other hydraulic actuator instead of or in addition to the above-described VVT required oil amount.
- the feed amount of work oil to the feed oil passage 5 becomes again the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 .
- the oil amount to the feed oil passage 5 exhibits a characteristics indicated by R-T line in FIG. 8 . That is, after communication is established between the valve port 41 and the first oil passage 61 , the feeding of work oil to the return port 42 is stopped. So, the feeding destination of the work oil which has been fed so far to the return port 42 is now changed to the feed oil passage 5 . Therefore, the feeding amount of work oil to the feed oil passage 5 increases ( FIG. 8 : R-S line) and thereafter the feeding amount becomes the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 ( FIG. 8 : S-T line).
- the return port 42 communicated to the return oil passage 66 is valve-opened and communication is established between the first oil passage 61 and the second oil passage 62 .
- a fourth communication passage 94 is formed by the second land 47 Y and the first inner wall portion 55 . Accordingly, it becomes possible to feed a portion of the work oil from the main discharge port 31 and a portion of the work oil from the auxiliary discharge port 32 to the return oil passage 66 via the fourth communication passage 94 .
- the third communication passage 93 too is formed by the bottom 48 b of the valve body 47 and the second inner wall portion 56 .
- the feed oil amount becomes the sum of a portion of the discharge amount of the main discharge port 31 and a portion of the discharge amount of the auxiliary discharge port 32 .
- the feeding oil amount to the feed oil passage 5 exhibits a characteristics indicated by T-U line in FIG. 8 . That is, as the route to the return oil passage 66 is communicated, the increase rate in the discharge amount relative to the increase in the rotational sped of the rotor 2 becomes smaller.
- FIG. 8 shows also the relationship between the required oil amounts for a piston jet as a work oil fed section 7 and the rotor rotational speeds.
- a total discharge amount comprising approximately the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 .
- the oil supply apparatus 100 is configured such that the slope of the characteristics curve T-U in FIG. 8 extends over the required oil amount W for the piston jet.
- the oil supply apparatus 100 may be alternatively configured that the slope extends over the required oil amount of any other hydraulic actuator instead of or in addition to the above-described piston jet required oil amount.
- the feed amount of work oil to the feed oil passage 5 in this situation becomes the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 ( FIG. 8 : O-P line).
- the excess work oil in the second oil passage 62 may be returned to the return oil passage 66 without being fed to the feed oil passage 5 . With this arrangement, the excess oil pressure can be lessened.
- the feed amount of the work oil to the feed oil passage 5 may be the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 ( FIG. 8 : S-T line).
- the feed oil amount becomes the sum of the discharge amount of the main discharge port 31 and the discharge amount of the auxiliary discharge port 32 ( FIG. 8 : S-T line).
- the characteristics shown in FIG. 8 can be set appropriately. Therefore, since the characteristics can be set in accordance with the relationship between the discharge amount and the rotational speed, there can be realized an oil supply apparatus 100 suffering less pressure loss, thus achieving high efficiency.
- the setting of point P, point S and point T can be varied also by varying the urging force of the spring 49 , instead of or in addition to the above-described setting methods. For instance, by increasing the urging force of the spring 49 , the point P, point S and point T can respectively be set to the high rotational speed side. By decreasing the urging force of the spring 49 , the point P, point S and point T can respectively be set to the low rotational speed side.
- the inventive oil supply apparatus 100 With the inventive oil supply apparatus 100 , with the two lands i.e. the first land 47 X and the second land 47 Y, communication states between the second oil passage 62 and the first oil passage 61 and the return oil passage 66 can be controlled. Therefore, in comparison with a valve body having three or more lands, compactization is possible. Further, since the total stroke length of the valve body 47 is shortened in correspondence with the compactization of the valve body 47 , the oil supply apparatus 100 per se can be formed compact. Accordingly, there can be realized an oil supply apparatus 100 having good mountability.
- the return oil passage 66 is an oil passage for returning oil to the suction port 36 .
- the application of the present invention is not limited thereto.
- the return oil passage 66 may be configured as an oil passage for returning work oil from the hydraulic control valve 4 to the oil pan 69 or as an oil passage for returning the work oil from the hydraulic control valve 4 to both the suction port 36 and the oil pan 69 .
- the present invention may be for use in e.g. lubrication of an automobile engine and controlling of a hydraulically controlled device.
- valve body 47 valve body
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Multiple-Way Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2010271289A JP5278775B2 (ja) | 2010-12-06 | 2010-12-06 | 油供給装置 |
JP2010-271289 | 2010-12-06 | ||
PCT/JP2011/075994 WO2012077458A1 (ja) | 2010-12-06 | 2011-11-10 | 油供給装置 |
Publications (2)
Publication Number | Publication Date |
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US20130209237A1 US20130209237A1 (en) | 2013-08-15 |
US8827659B2 true US8827659B2 (en) | 2014-09-09 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US13/878,626 Expired - Fee Related US8827659B2 (en) | 2010-12-06 | 2011-11-10 | Oil supply apparatus |
Country Status (6)
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US (1) | US8827659B2 (pt) |
EP (1) | EP2628954B1 (pt) |
JP (1) | JP5278775B2 (pt) |
CN (1) | CN103237989B (pt) |
BR (1) | BR112013014073B1 (pt) |
WO (1) | WO2012077458A1 (pt) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US20170284242A1 (en) * | 2014-11-19 | 2017-10-05 | Aisin Seiki Kabushiki Kaisha | Relief valve |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
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KR101551102B1 (ko) * | 2014-07-01 | 2015-09-08 | 현대자동차주식회사 | 엔진 오일펌프 |
DE102014222396A1 (de) | 2014-11-03 | 2016-05-04 | Continental Automotive Gmbh | Verdrängerpumpe |
JP6411228B2 (ja) * | 2015-01-19 | 2018-10-24 | アイシン・エィ・ダブリュ株式会社 | 伝達装置 |
JP6502725B2 (ja) * | 2015-03-31 | 2019-04-17 | 株式会社Subaru | オイルポンプ装置 |
CN108223357B (zh) * | 2017-11-24 | 2019-11-08 | 河南航天液压气动技术有限公司 | 一种内泄式齿轮泵 |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170284242A1 (en) * | 2014-11-19 | 2017-10-05 | Aisin Seiki Kabushiki Kaisha | Relief valve |
US10301983B2 (en) * | 2014-11-19 | 2019-05-28 | Aisin Seiki Kabushiki Kaisha | Relief valve |
Also Published As
Publication number | Publication date |
---|---|
BR112013014073B1 (pt) | 2021-01-12 |
EP2628954A1 (en) | 2013-08-21 |
US20130209237A1 (en) | 2013-08-15 |
EP2628954A4 (en) | 2013-10-02 |
WO2012077458A1 (ja) | 2012-06-14 |
JP5278775B2 (ja) | 2013-09-04 |
CN103237989A (zh) | 2013-08-07 |
JP2012122341A (ja) | 2012-06-28 |
EP2628954B1 (en) | 2014-10-15 |
CN103237989B (zh) | 2015-09-23 |
BR112013014073A2 (pt) | 2016-09-20 |
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